Counterbalancing device



Sept. 16, 1952 FREDERICK K. MAUSSNEST NOW BY CHANGE OF NAME FREDERICK K. MAUST COUNTERBALANCING DEVICE 5 Sheet s-Sheet l 1 Filed June 25, 1948,

%:EN TOR v NOW BY CHANGE OFNA E Fmsoealcz K MAU6T S pt. 1952 FREDERICK K. MAUSSNEST 2,610,524

' NOW BY CHANGE OF NAME FREDERICK K. MAUST COUNTERBALANCING DEVICE HIIH m.

' INVENTOR.

No my camera ME Fzsoamcz I MAUST' Sept. 16. 1952 FREDERICK K. MAUSSNEST NOW BY CHANGE OF NAME FREDERICK K. MAUST COUNTERBALANCING DEVICE 5 Sheets-Sheet 5 Filed June 25, 1948 a w M 9 NM m 5 T w I a I K N Z i w m UNI??? Y WI, 5% e Mm fa. i WIIIIIIIIIIIIII/A Sept. 16, 1952 FREDERICK K. MAUSSNEST NOW BY CHANGE OF NAME FREDERICK K. MAUST COUNTERBALANCING DEVICE 5 Sheets-Sheet 4 Filed June 23, 1948 LQ Q IN VEN TOR.

New 'BY CHANGE OF NAME fmfoemcz K. MAUT Patented Sept. 16, 1952 rem" OFFICE CQUNTER BALANCING DEVICE Frederick K. Maussnest, Queens Village, N. Y., now by change of name Frederick K. Maust Application June 23, 1948, Serial No. 34,645

4 Claims.

This invention relates in'general to balancin devices for completely counterbalancingcrank actuated reciprocating mechanisms, 1. e., mechanisms for changing a substantially uniform rotary motion into a reciprocating motion, or vice versa, and more particularly to balancing means for punch presses of all kinds which employ driveshafts with crankarms or crankpins, or driveshafts carrying, eccentrics or eccentrics mounted on bull gears, herein simply called crankshafts, in combination with connecting rods or sliding blocks for reciprocating their working heads or slides.

The term punch press is used. hereinafter in itsbroa'dest sense and. includes any and all mechanical presses Whose slide or slides are reciprocated by crankshafts with single cranks or multiple cranks or eccentrics, defined in this art as single crank presses, double crank presses,

multiple slide presses, four point suspension presses, etc.

Mechanical punch presses are nearly exclusively built on the above described crank principle because of the many advantages of construction and simplicity of design. Crank motions of this type are, however, unfortunately The cost of constructionof such equipment compared with conventionalpresses of similar tonnage capaciti app-ears out of proportion coinpared with theresults obtained.

The unbalanced forces encountered in the operation of a reciprocating crank mechanism or kinematically equivalent system, such as a punch press maybe conveniently divided into three distinct classes.

2 caused by the reciprocating slide with its associated elements. short "primary and secondary inertia forces.

.While ,the reciprocating inertia forces of such crank actuated reciprocating systems which employ pitmans have theoretically an infinite number of harmonics of even number, only the first and second harmonics will beconsidered here, because they represent very nearly the true slide motion. The frequency of the harmonic hes the rate of rotation, the first harmonic having crankshaft speed, the second harmonic having twice crankshaft speed. The secondary inertia forces already are of comparatively small magnitude, i. e. equal to the primary inertia forces divided by the ratio of connecting rod length over the crank radius. This ratio is usually on the order of, about 10:1 to 15:1 in punch presses. These figures are not given in any limiting sense,

but only to 'make visualization of the relative forces easier.

The slide motion of presses which employ a sliding block surrounding an eccentric is a simple harmonic, because the connecting rod of finite length is eliminated. The total inertia forces of the reciprocating mass are therefore simply the primary inertia forces.

3rd: In addition to the dynamic inertia forces which appear as a result of the motion of the machine, the static weight'of the reciprocating slide assembly exerts a steady and constant downward force in a vertically placed crank mechanism of this character.

To obtain complete balance, all inertia forces and the static weight of the slide assembly must be counterbalanced by equal and opposite forces. Otherwise the unbalanced forces will act on the crankshaft and consequently on the main bearings of the machine, thereby increasing the 1st: The unbalanced rotational inertia forces.

caused bylthe rotating 'crankarm or, crank'pih"v including those associated, elements which may,

be considered as partaking ofitsrotary motion.

ized by masses attached to the crankshaftdiametrically opposite the crank-pin at aradiu's that .50 These rotational inertia forces may be neutral-- cushions.

bearing. load and setting up forced vibrations. The latter not only limit the speed of operation,

'but must be absorbed by the main frame or has foun-d little application in punch presses 'b'e' cause'of space limitations and particularly for the reason that this method alone accomplishes atloest only a partial solution to the existing vibration problems. of counter-balancing the -unbalanced static and dynamic forces in presses has been heretofore restrictedto single or compoundsprings or air These forces will be called in,

Therefore, the usual extent It. is obvious that silnple harmonics I witlrdiilerent frequencies cannot be oounterbalwhich act in opposition to the rotational and reciprocating inertia forces, respectively,--and by air cushions or springs for neutralizing the static weights, as will be fully shown and describedhereinafter.

More specifically, one object of my invention is to provide balancing means .for reciprocating crank systems. of the character described for neutralizing the rotational and the primary" inertia forces by employing" two or more" counterweights which revolve synchronously with the drive shaft or crankshaft; at l'e'ast'oneoi said counterweights beingadapted to revolveiin the same direction and at the same" speed as the crankshaft; andat least one other'counterwei'ght being adapted to revolve at th same speednut in opposite direction to the crankshaftL Another'obj ectis to prcvidelthejust mentioned balancing means with additional counterweightingm'eansa'dapted to rotate at twice crankshaft speed rcr: also neutralizing? the secondary inertia forces;

A further object is to provide compact, selfcontaine'd-balancing units which may be conveniently attached singly or inmultiples to punch presses or other equipmentto be balancedand inwhich bevel gearing is employed for imparting the proposed directions and speedsto the counterweightingmeans.

Another object is to provide novelly arranged-- air cushions and/or springs in conjunction withpunch presses for off-settingthestatic weight of the slide assembly.

These and other objects andadvantages: will become better understood as the following description of certain present preferred embodimentsproceeds. In the accompanying drawings Ihave shown by way of example saidpresentpreferred embodiments, inwhich Fig. 1 is a right hand sideyiewalong line li of the balancing unit shown in Fig. 7 (press frame: and mounting: boltsnot shown) for ofi settingrotational as wellasprimary inertia forces. 7

Fig. 2- is a section-along line 2-2 inliig; 1. Fig. 3 showsa partial end view taken along The novel balancing means line33- of Fig. 2 and'isiintendedto depict specifically the bearingbracket for the pinion :shaft'.

Fig. 4 shows a modification of the bevel-gears Fig. 8 is a cross-section of an air cylinder along line 8-8 of Fig. '7.

Fig. 9 shows diagrammatically the connection of the air cushion to an air tank.

Fig. 10 shows an underdrive punch press with twin balancing units and. separate counterweights on the cheeks of the crankshaft together with springs arranged concentrically with the guide rods foroff-setting the staticweight.

Fig. 11 illustrates a right'hand side'view of the balancing unit employed in Fig. 10 as seen along line H--H of Fig. 10, press frame and mounting bolts not shown.

Fig. 12 is a cross-sectional view along line IZ-llofFig. 1.1.

.F'ig; 13 shows -agpartial left hand side view of the balancing unit illustrated in Figs. 11 and 12.

Fig.- 1-4- depicts'one of the counterweights on thechecks of the crankshaft along line I l-M ofFig. 10.

Fig. 15 is avertical cross-section through the balancingunit. along line l5l 5 of Fig; v18,press frame ancl mountingbolts not'shown'.

Fig. l'fii-is a horizontal'cross-section through the sameunitalongiline l 6'l 6 of Fig. 18.

Fig; 17' shows a double crank press with centrally' lo'c'ate'd balancing unit, partly in section a1ong'1i'ne;|1 ITof Fig; 18.

Fig. 18' is a fragmentary" section alone line Iii-i8 of Fig; 17 depicting the. crown andslide ofthejpress".

Fig." 19' shows a'fra'g'mentary section of the crown of the press shown in'Fig; 18, exemplifying the use of air cushions instead of springs.

.Fig'. 2 0'il1ustrates' the application of twin balancingunitsiinside thepres's' frame of a double crank press of which only'a fragmentary front elevation is shown.

Fig. 21 shows a partial front view of a single crank press with twin balancingunits mounted inside thepres's' frame.

Fig. 22 also depicts a partial front view of a single crank press with twin balancing units on the'outside'of the press frame.

Figs; 231.24, 25', and.26 show'diagrammatically the relative positions of the rotating counterweights'for neutralizing'the primary and the secondary inertia forces with the crankshaft in the 0; and 270 positions, respectively.

Referring now moreparticularly to the drawings, the relativep'ositions of the counterweights for neutralizing. the primary and secondary inertiaiforc'es'.areshown diagrammatically in Figs. 23' to 26. In Fig. 23the crankpin or crankarm P is at top dead center' which is designated as the 0 position. The. crankshaft S is assumed to be rotating" counterclockwise direction. The counterweight or" mass A rotates in the same direction'and atthesame speed as the crankshaft S and is located" diametrically opposite the crankpin P; i. e; at bottom dead center'at this instant. counterweight B'rota'tes'in opposite direction to crankshaft S but'at'the same speed and is coincident in this crank position with Weight A at bottom dead center; These two counterweighting masses A and'B; rotating at crankshaft speed but in respective opposite directions, will completely neutralize, oppose or counterbalancethe primary inertia forces, provided their radii of rotationand theirirespective masses are so chosen A is located' opposite the crankpin P so that a repeats itself.

During one complete revolution of the crankpin counterweight for neutralizing the rotational in= ertia forces may. be conveniently combined there= with, if desirable. 1

The counterweight C rotates in the same direction as the crankshaft S but at twice its speed.

counterweight D rotates in opposite direction to the crankshaft and also at twice its speed. Coun= terweighting masses A, B, C, and D act vertically downwards with no horizontal force components and are coincident at bottom dead center in the 0 position of crankpin P. "Theradii of rotation and the masses of counterweights C and D are preferably so chosen that each. mass neutralizes substantially one-half of 'the secondary inertia forces to be counterbalanced.

Fig. 24 depicts the crankshaft S after having made one quarter of one revolution, having thus arrived at the 90 position. Counterweights A and B also have advanced 90 in their respective directions of rotation and have arrived at the 270 and 90 positions, respectively. Their centrifugal forces have no vertical components and act horizontally in opposite directions, thus cancelling each other. Masses C and D are in the 0 position and act vertically upwards without horizontal components.

Fig. 25 shows the crankshaft at bottom dead center (180) position. Counterweights A and B are at top dead center and their centrifugal forces act vertically upwards with no horizontal components. Masses C and D are at bottom dead center; their forces act vertically downwards with no horizontal components.

Fig. 26 illustrates the positions of the several counterweights with the crankshaft in the 270 position. The masses A and B act in horizontal, but opposite directions and therefore cancel each other. They have no vertical force components. Counterweights C and D have arrived at top dead center and exert vertical upward forces without horizontal components.

After another quarter'revolution, the crankoriginal positions shown in Fig. 23 and the cycle Pfall balancing weights are coincidentat bottom dead center whenthecrankpin P isat top .shaft and counterweights assume again their dead center; masses A and B are coincident at top dead center with the crankpin at bottom dead center;' counterweiglnts C and D are coincident at top'dead center with the crankpin in the90 and 270 positions; masses Cand D are also coincident at bottom dead center when crankpin P is at bottom dead center.

While the positions of the several counterweights have been shown for full quarter revolutions of the crankshaft only, it will be obvious. fromthe diagrams that the symmetrically artudes and directionsfas"to oppose and thus Ielim- 'inate the harmful primaryan'd secondary inertia forces .of reciprocating crank systems. ,Mean's will be described hereinafter'to actuatejthe several counterweights at the speeds and in the directions diagrammatically indicated inFigsL23 to 26 in positive synchronism with the crankshaft.

rotation. Consequently, a.perface balance may be accomplished at any operating speed, because 6 it is axiomatic that if the mechanism is brought into balance at one speed, it will also bein balance at any other speed.

Figs. 1 to 3 show a balancing apparatus for opposing the rotational inertia forces and the primary inertia forces. The unit may be mounted directly on a crankshaft 2| which may be in top dead center position as indicated in Fig. 1 by the numeral 20. On the driveshaft 2|, two bevel gears 22 and 23 are mounted in face-toface and spaced relation and are in mesh with a right angle bevel pinion 24. Bevel gear 22 may be secured to shaft 2| by a key 25, while gear 23 is'fre'ely' rotatable on bushing 26. When shaft 2! is rotated, bevel gear 22 will rotate in the same direction as crankshaft 2| and gear 23 will be forced to revolve at the same speed but in opposite directionthereto. Bevel gears 22 and 23 are equipped with'ann'ular pockets 2! and 28 for carrying counterweights At and B, respectively. These counterweights may be fastened to the bevel gears in any desirable position by means of bolts 29 or the like in the annular pockets 2'! and '28. With the crankpin 20 at top dead center, they are preferably located coincident at bottom dead center position as shown. Both counterweights may possess the same radius of rotation, but mass At is shown considerably larger than mass B. According to previous explanations, the two counterrotating weights A and B in Figs. 23 to 26 should preferably be adapted to cause centrifugal forces of substantially the same magnitude, and hence, with identical radii of rotation, their masses should be equal. However, as also pointed out previously, the rotational inertia forces may be neutralized by a suitable counterweight or counterweights attached to the crankshaft diametrically opposite the crankpim The additional mass required for off-setting the rotational inertia forces is therefore shown combined with the weight A of Figs. 23 to 26, resulting in the mass At whose weight is such as to neutralize substantially onehalf of the primary inertia forces plus the rotational inertia forces.

When equal centrifugal forces of necessary magnitudes are developed by masses At and B, this balancing unit will counteract the primary inertia forces only, as pointed out above. Equal centrifugal forces will be produced when employing balancing masses of the same specific gravity, equal size, and identical radii of rotation; or by maintaining the relative sizes and eq'ualradii of rotation of At and B as shown in Fig. 1, but selecting for At a material of lesser specific gravity'than for B; orby reducing the radius of rotation of mass At as compared with that of B by such means as will be described in connection with Figs. 4, 5, 6; or by a combina tion of some or all of these expedients.

Pinion 24 may be keyed to shaft 39 which is rotatably mounted in thrust bearing 3| and ball bearings 32 of bearing bracket ,34 fast to bellshaped casing 35 by means of bolts 33. Casing 35 may be conveniently provided with a front cover 36 secured thereto by bolts 39. To prevent leakage, seals 3'! and 38 maybe placed aroundthe driveshaft 2!. Housing 35 may, have a flange with boltholes 4! for securing the balancing unit to a stationary part of the machine to be balanced.

' Figs. 4 to 6 show a modification in the mounting of the counterweights which may be employed for any balancing unit. An eccentric sleeve 42 is adjustably mounted on the hub 43 of the bevel gear 44 and provided with a series of tapped bolt '2' holes 45. whose-centers are onia. circleaooncentric withzhub: 43. for fasteningthaeccentric: 42 i ini anydesired angular position to the-web of bevelgear M; bymeans' ofi bolts fifiextending through matching. holes in..the wehof the bevel; gear. Casing i1; is: disposed on eccentric sleeve: 42 and: provided with. a suitable pocket forreceivingsthe. counter-- weighting mass, 48'; whichmay consist of' any heavy" substance;,. such. as. lead, held in. place by cover 49. and boltsfifl; Casing 41. is equipped with a flange? 5;! having" threaded. holes. adapted. to receive. bolts; 52 extending; through. slots 53' in the-web. oibevel gear... Any-number: of addi:--

tional suitably" located slots; as; indicated by 5.4.

may be arranged :tor; the; angular;- displacementof' tires. counterweight.

Figs. Landfi-show'the counterweight 48- in the position nearesti the axis ofrotation. of-shaft: 55.

By turning theeccentricsleeve 42., theradius of i rotation of. the: counterweight may be increased, whereby'the centrifugal counterbalancing force. produced by the. counterweight: is increased ac:-

cordingly. To compensate for this radial displacement, openingsz53 and.5.4 araof slot shape;

The; eccentric and; angularly adjustable mountingofthe counterweight 48 above described may be: ofqspecia'l advantagawhen the. balancing units are; employed in corrjunctionwith presses-having adiustableastrukm. The; proposed changeability of the. balancing effect" also will facilitate the a adaptationof; onerzsize balancing unit'to a range of: diiierent; machine sizes;

Fig. 7. exemplifies .a possible application ofithea balancing: unit; of Figs. 11 to. 3. to. a punch. press witlrunderdriva. The press: may be. driven by beltsfr'omany POW611.SD11I.C8C such. as an electric motor: (not shown) on the. clutch-flywheel; whichis carried: by" crankshaft: 2 l-. A pitman or connecting rod. 51- extends; between'icrankpin 26 and lower cross-head, 58: for reciprocating the latter. These presses-are. usually-of square or'rectangular. form and four rods 55 of. cylindrical cross-section, suitably guided in' split tapered bushings'fiil, transmit. the reciprocating motion of the lower cross-head 58 to the upper cross-head or slide 6| on which a punch. 6'2 is fastened which cooperates with a die. 6.3 normally supported on the..- bed or. table 64: forming. a part of the press frame 65. M indicates the-work-material fed between punch and die either by'handor automatic feed (not shown) for. performing thereon any desired operationsuchasblanking, stamping, drawing, embossing; etc. Upper and lower cross-heads GI. and 58- are shownadjustably guided on press frame=65 by means of gibbing, generally indi ated by 66. Crankshaft 2i is. journalled in bearings 61- andhas attachedto it abrake 6B. for stopping theslide approximately in. topdeadcenter posi-' tion. of crankpin. 2il when the-flywheel- 56 is declutched. This press. or any. other press shown and. described. hereinafter for exemplifying the application of; the. balancing means forms per se no. part of the present. invention.

Twin balancing. units 6'9 and 19 may be flange.- mountedto the outsideoithe press frame 65 (Fig, 7) by'means of'bolts H; Each one of the guide. rods. 5.9 may carry a piston 12 pinned or otherwise fastened thereonand slidably guided in a cylinder 13 whose upper endflis shownsecured to the underside of table 64 by bolts .l iand has passages 15 communicating with the atmosphere (Fig. 8).

A chamber-is formed between piston 'lzand lower cover 16 and sealed by packing or piston ring-1T and annular-sealp'lfl. As diagrammatically'shown in Fig. 9', pressure fluid such as oil or preferably compressed air otsufiicient pressure,

8; from-any suitable source not shown, is: admitted to' the chamber from atank T9 to counterbalance the static weight of the reciprocating slide assembly; comprising. the. upper and lower cross-heads 6.1 and 58.; guide rods 59, punch 6-2", etc. The-pressurein tank l9maybez'conveniently regulated bymeans of; pressure: regulating valve and pressuitegaugezfll. 'Ilankas. well as control valve and gaugexsmay' be. located: wherever convenient; but

itis pointed out; that: the cylinders 13 are in directzcommunicationwith tank 1.9 by conduits-.82. As. tank: 19: is of; comparatively large volume, the air pressure in: cylinders: 13 remain. substantially constant at. all. times;

All four guide rods; .59..may'bez arranged with concentric; air cushions: 1.3. as shown, or only" two diagonally opposite guide; rods. may be so arranged; depending: on; the size air cylinders em ployed, the-available-maximum. air-pressure,- and the. weight. of irthe .reciprocating slide assembly.

The-n0vel.m0unting-:of:the .air: cylinders T 3 under-- neath theipressrtable 6.4.2 and. concentric with theguide rods 5.9. results; in; advantageous space utilization and simplified construction.

For. certainpunch; press; operations, itmay be desirable to overloalancezthe.staticwei'ght for-thepurposeofj ,takingiuprranyexisting play in. the

bearings andot-her operating: elements of themachineto. controlthepenetration: of the; unchmore-closely. While ithaaircylinders. shown may be. conveniently employed for: this purpose also.

this is. a. consideration which is: not part ofithebalancing prob1em..

Themasses. of. the; 'counterweighting means in balancing units' -69:and;1l)"are preferably so chosen:

that. each. one: of. the balancing units; neutralizes substantially one-half of the: total; existinggrotational and primary' inertiaforces. The. counterbalancing of.- thestatic weight mayalso; be evenly distributedamong the total number of. air- Thistype balancingdeviceis. capable, however.

of completely counterbalancing the inertia forces of. the reciprocating-slide assembly of a press which. employs a slidingblock. surrounding thecrankpininsteadof a pitmanoffinite length.

Figs. 10 to 13 illustrate a somewhat simplerbalancing unit andits application-to anjunderdrive. punch press, similar to thatshown andidescribed in conjunctionwithFig. '7. Tosimplify the. description, similar elements have received identical. numerals. as. before with the: letter :1. attached for differentiation. One difierence betweenthe. designsof the presses, shown in Figs. 7 andlO is that the upper. cross-headfila of Fig. 10 isnot guided on the. press frameBEa.

It willbe seenthat only the counterweighting.

mass. Ba. is. incorporated. in the. balancing unit proper. Thismass Bcisrotated in. oppositedirection to. and at the samespeed as the crankshaftZI'a for offesetting. one-half of the primary inertia forces. Other counterweights and 98 are attached directly tothe. crankshaft 21a for neutralizing the rotational inertia forces and. the

remaining one-half.of;the primary. inertia forces.

In Figs. 11 to 13 the bevel gears. 22a. and 23a. are geared. together by pinion 24a as before. Bevel gear 22a is again keyed to .driveshaft Zla but carries no counterweight. Bevel gear 23a This? ings 26a'and is equipped with a pocket 28a for carrying mass Ba. Pinion 24a is keyed to shaft 300 and free to rotate in radial thrust bearings 32a which are mounted in suitable bores of projections 83 formed on one side of the horizontally split housings 35a and 36a. A cover 84' serves to seal the opening in the casing. Lower and upper casing halves 35a and 36a carry flanges 85 and 86 along the horizontal split line and are secured tightly together by a series ofbolts 81. The rear parting lined the casing halves 35a. and 36a maybe formed inthe shape of'an interlocking V shoulder 89, and both said halves may be provided with circumferential mounting flanges 40a for securing the balancing unit to the machine frame 65a by means of bolts Ila, as shown in Fig. 10 for balancing units 93 and 94.?

The auxiliary counterweights 95 and 96 may be mounted on the crankshaft 2Ia at any convenient location but are shown attached to the cheeks of the crankshaft adjacent to the crank pin 20a. One of the counterweights is shown in detail in Fig. 14 and may consist of a lower half 97 forming a pocket for carrying massAts which is held in place by a cover 99 and screws I00. The counterweighting means are clamped to. the crankshaft by means of bearing cap IOI', bolts I02; a key I 03 maybe provided for positive location with respect to the crankpin 20a.

The masses Am and their radii of rotation are preferably so chosen that their combined centrifugal forces oppose and neutralize the total rotational and substantially one-half of the primary inertia forces. These two counterweights and 96 correspond therefore in their balancing effect and function to the weight At in the balancing unit of Figs. 1 to 3; counterweight Ba is directly comparable to mass B of Figs. 1 to 3.

The 'counterbalancing of the static Weight of the reciprocating slide assembly is shownto be effected by coiled compression springs I04 placed concentrically with guide rods 59a and acting against spring seats I05 securedto rods 59a by pins I06. The other ends of the springs rest on seats I01 .which are vertically adjustable for preloading purposes by means of threaded nuts I00 and rods I09 are shown. I

A similar balancing effect could, of course; be obtained by choosing the masses Am on the cheeks of the crankshaft of sufficient magnitude, only to off -set the rotational inertia forces. Then balancing units of the type shown in Figs. 1 to 3 would be required but with masses AI; and B for developing, centrifugal balancing forces-of substantially equal-magnitude by employing such expedients as pointed out in connection with Figs. 1 to 3. The balancing units would then neutralize the primary inertia forces and v the auxiliary weights on the crankshaft would off-set the rotational inertia forces. The counter-' weighting masses rotating in crankshaft direction within the balancing units and thecounterweights directly. attached to the crankshaft (55.06) may. also be proportioned in any other desirable manner as long as the total centrifugal counterbalancing forces of all the counterweights revolving at crankshaft speed and in crankshaft direction are substantially equal and oppositeto the rotational inertia forces and to-one-half of the primary inertia forces.

Space is consumed for swinging the counterweights 95 and 96 on the crankshaft cheeks. For certain forming and drawing operations, air

cushions or spring attachments must: be placed -10 underneath the press table 64a, for which reason the balancing system shown in Fig. '7 is generally preferred.

Figs. 15 and 16 exemplify a balancing unit I46 adapted to neutralize primary and secondary inertia forces as well as the rotational inertia forces. Therefore, in addition to the balancing masses Au) and B2) rotating in respective opposite directions at the frequency of the first harmonic,

i. e. at crankshaft speed, other balancing weights I C and D are provided to rotate at the frequency of the second harmonic, or at twice crankshaft speed. Balancingunit I46 is shown split along the horizontal center line as previously shown in Figs. 11 to 13, with the exception, however, that two bevel pinionsv 2412 are employed to distribute the load. Both bevel gears 22b and 23b are equipped with annular pockets for receiving the counterweights Au) and Bb in a similar manner as shown and described in connection with Figs. 1 to 3. To simplify the description, similar elements have therefore received the same numerals as in the preceding illustrations with the letter .b attached for differentiation.

The two counterrotating bevel gears 22b and 23b carry internal gear rings H0 and III which mesh with pinions H2 and I I3, respectively. Stub shafts I I4 and I I5 fast in suitable bosses I I6 and II! and secured by'washers I I8 and H9 and bolts I20 and I2! revolvably carry said pinions I I2 and H3 on suitable bearings, such asneedle bearings I22 and I23, respectively. Pinions H2 and H3 are in turn in mesh with gears I24 and. I25, respectively, which are freely rotatable in bearings I26, I21 on the hubs ofbevel gears 22b, 23b. Gears I24 and'l25 may form annular pockets for carrying the counterweights D and C in a similar manner as previously described in connection with the counterweights Am and B1). The several counterweights of Fig. 15 are shown to be enclosed in containers'aas indicated at I28 with a cover I29 andboltsl30 threaded into the web'of the gears for conveniently locating said counterweights. Should it be desirable to displace the counterweights in the annular pockets, additional holes may be drilled and tapped'for said bolts I30.

Assuming that the crankshaft I3I rotates in counterclockwise direction as viewed from the right in Fig. 1 5, bevel gear 221), internal gear ring H0 and pinion I I2 will also rotate in counterclockwise directions, whilegear I24 with counterweight D will revolve in clockwise direction. Bevel gear 23b, gear ring III, pinion I|3will rotate in clockwise directions and gear I25 with counterweight C in counterclockwise direction. The numbers of teeth in respective gear rings I I6, III, pinions H2, H3, and gears 124, M5 are so selected that gears I24, I25 are caused to rotate at. twice crankshaft speed. Thus the directions and speeds of rotation of all counterweights diagrammatically shown in Figs. 23 to 26 have been realized in practice.

Figs. 17 and 18 show a straight sided double crank press of tie-rod construction with a dentrally disposed single balancing unit i i-6 of the type shown in Figs. 15 and 16. This press is called double crank press in the trade, because the driveshaft or crankshaft I3t is equipped with two crankarms or crankpins I32 and two pitmans I33 for reciprocating the slide I34. The clutchfiywheel I35 is mounted on one end of the crankshaft and a brake I36 on the opposite end. The crown I31, housings I35, and bed I39 are usually tied together by four tie-rods and nuts I if. The

gel 6,524

.11 static weight of :the' 'slide=-assemb1y including" the weight of. any-bolster-plate,-die etc. whichtfmay be secured thereon (not shown) is counterbalanced by means of coiled compression springs IAI-locatedin achamber'I' I-Z, formed in crown I31. ;-Rods-l43 extend between spring seats I44 and slide] Stand are adapted for varying thepreloading ofsprings MI by meansof-nuts I45. A series of bolts I secure the balancing unit M's-to croivvnJS'I.w

V Fig, '19- illustrates the application; of pivotally mountedair, cushions or air cylinders I48 (instead of springs iI4I) to-the 'press' of Figs. 17 and 18. The basicarrangement:iszidehtical to that described -i,n conjunction ewithiFigs; 8 rand-.9 rand needsno explanations. .;The 'aircylinders I 28'are free tofturnion pivots;I;49suppoi'ted in'the wall of crown I31:and-inthe loracketsmflfiil bolted to the "crown as indicated. at I5 I. The top. of the air cylinders is open to" the atmosphere thrugh nerturesgltfi. r

, Fig, I 20- showszthe application-of twin balancing units I-EB'andI 54 toiasimilar ddublie crank press as shown in FigSrl'hil-B. -Tliese,balancingunits are securedto the inside ;of :th'e press frame by means 'o'fjbolts I 52. 'iDepen-ding on? the degree of counter-balanc n "required, the units: ma he: of thetypeishowminrFigsrl tie-:3 or Figs; and'fi.

{The static Weight of :theslidei'may' betccunte'r balanced :by 'meanspt air cfushicns according to Fig. 19 or by; springs as shown-in Figs. l'l'and I8. Similar. parts have received the same numerals as inFigs-lf? andgl-8 with'the'letter cf attached.

Fig. 21; exemplifies the provision of twin balancing units 'to the' inside of the press frame of a single. .c fank;punch-press and corresponds directly to; Fig.520. Similar elements have received identical numeralsj'with the letter d attached. Thecrankshaft I3Id; carris"at its 'left'end an adjustable crank; disc ea'wh'ich'is frequently-em ployed' for actuating' an automatictfeedsuch as a roll, feed (not. shown) forfee'ding the work material intermittently between punch and die. Fig.. 22 showsa: Single crank press provid'ed'with twin balancing units flfland :9I on-th'e' outside of the, pressframe. The units are of'th'e "type illustrated in Figs. 1 to 3 and secured to the" press frame byme'ans of boltsllc. The staticweight of the-slide assembly of this or any'of the other presses shown may,bef'counterbalancedhyfneans of springs or aircushionsias previously described. Similar elements: as shownbefore'have again re"- ceived the samenumerals with the letter e attached to simplify the; description. 1

Likely locations for mounting the balancing means have been shown in conjunction with several popularpress types. It is expressly understood, however, that .these locations wereselected as examples only. The balancing means'should be located where most convenient and effective in any one of the multitude of particular-press designs knowninthe art. 7,

For instance, the baIanci-ng'unitsI-Eii and I54 of Fig. could belocated on the outside of the press frame as showninFig. 22 ;10r two additional balancing units, besides units I53 and I54,'may be provided on the outside of the press frame, thereby dividing the balancing task'among four units. In addition to the centrally located balancing apparatus I46 in Fig. 17, two more balanc ing units may be appliedto the inside of the press frame as shown in Fig. 2. and/ or two additional units may be provided on. the outside of the press frame asshown inFig. 22, or any desired combination thereof" may be employed. When multiforces.

pleshaming" umtsareusem they are-preferably,

but not necessarily, locatedsymmetricaliy :to 'the crank and each on mayZ'EOntributeequaliyi to neutralize ithe*totail 'zexis'ting unbalanced inertia The use of 'multiple 'units obviously psi" mits'a decrease in size for each uniti: ,.T.' 1

While thei'counterweightor coimterweights for ofisetting the rotational inertia forces may be advantageously combined :with the fbalancing mass in the unitwvhich"rotate sinthiesainredire}: tion and at 'the samespe'ed'as the crank sliaftg'this is not essential as efiemplifiedih Eigrlili rill-rider driv'e punch: presses' m'ayr have their spa-lamina devices located inside. the pfessframe-"synonymous to Figsrl'iylB; 20, Land Zrinsteadcf-pn-t outside as illustrated hi i igs-.7*and10. .i:

The actuation oft-thecounterrotating liallarming weights at crankshaft-speed-bysnieans"ofjbevel gear trains results -in atmosh-compactdesigrfancl destroys the harmfulineftiarforces"directly :on the crankshafton whichtheyrareracting; thus assuring smooth and vibra tionless 'opratifin :Of the machine at'high-speedsgfeducing bearing pressures andprolongingbearing life; Ihe'hevel gears may be of the straight;-'spiral,-"sl;ew-,;hypoid or other suitable .type. Thegearing-"for:irnp'art' ing twice crankshaft speed ."toTthosg-floalaircing masses which" offsetthe?secondaryineftia forces may have spur,hlicalor hefringbon type Other driving means maybe B phyethfor the several 'counterwightasuchas :beltsor-ordinary gearing thrm ighout, or a combination; {of

Regarding compactness of' designrreferene ts made to Figs. -1 'tEYB-"in"whichthe 'cdunt'errotating weights At and 13 are placed" between thetevel gears, thus utilizing; the space irequiredby tlie bevel'pinion'; orto Figs--15 and"16;where-=com pactness is achived-inasimilar;if slighfly -dif= ferent, manner 'and where the'resp'ective: "orbits of the primary and: secondary"cdunterweightsmb, Eb and D, C, respectively,-are so -chosen asto nest them.

Any one of the balancing units-shiiwn'andde scribed, or any combination thereof,=-'ma"y be'suh stituted for. the specific units? applied con junction w'ithFigs. 7, 10,"17;l8;*20;=21; ahd 22 m obtain either complete neutraliizatiorriof'jalrrota"; tional, primary and secondaryunertlaforces-or any lesser degree-of 'coii'nterbalance desired. 7

'Many modifications will -'be'-obvious to'those skilled in this'art. v With theseveral" exam lesshown, only ordinary skillwi'lhbe'requi'r ed toad ply the teachings of this invention twany cra'hk actuated reciprocating r'necha'rfism 'or kirieifiatF cally equivalent system. ing difierent d'gres' 'of obtained bystfippiiig of Figs. '15 "and '6 c ims e r geeeihef t rang me'nt is leftas namely, one counter gh r posite dirctionto, but-at the same speed asth crankshaft. I V v limit 1151 with m raii tifi irk. e hew rfle z 1 1at r 1 n th t h in en awa a s. ed out byo'ther means,;and* app; icd t0---uses other than above set out. It will" alsmbe-understood that all of the features of the-inventiomneed-not be used conjointly as -;theymay-"b'e-used to -ad vantage various combinations asdefiiied by the appendedclaims. w

Iclaim:

1. Balancing means for mechanisms having a driveshaft including eccentric or crank means as well as connecting rod means for reciprocating a slidecomprising at least one pair of balancing masses, means for rotating said masses in respective opposite directions around said, driveshaft at the frequency of the first harmonic, the mass rotating in driveshaft direction'being of such magnitude and having a radius of rotation as to produce centrifugal forces adapted to oppose and neutraliz the rotational inertia forces and substantially one-half of the primary inertia forces, the mass rotating in opposite direction thereto being of such magnitude and having a radius of rotation as to oppose and neutralize the remaining one-half of the primary inertia forces, auxiliary balancing masses, gearing means associated with said auxiliary masses and operatively connected with said rotating means for imparting to said auxiliary masses a rotational speed around the driveshaft equal to the frequency of the second harmonic to oppose and neutralize the secondary inertia forces.

2. A balancing apparatus of the character described comprising a pair of bevel gears disposed on the crankshaft of a machine to be counterbalanced, a counterweighting mass associated with each of said bevel gears, means for rotating said bevel gears with their associated counterweighting masses in respective opposite directions at the speed of the crankshaft, said counterrotating masses being adapted to. create centrifugal counterbalancing forces of substantially equal magnitude and such respective directions as to oppose and neutralize the primary inertia forces, 7

other counterweighting masses located diametrically opposite the crank of the crankshaft and adapted to be rotated with the latter and to neutralize the rotational inertia forces, an internal gear ring secured to each of said bevel gears, a gear freely rotatable on the respective hubs of each of said bevel gears, a pinion meshing with each of said associated internal gear rings and gears adapted to rotate said gears at twice crankshaft speed, and a counterweight secured to each of said gears for counterbalancing the secondary inertia forces, said counterweightingmasses and counterweights being coincident at bottom dead center when the crankshaft is at top dead center.

3. A counterbalancing device for a punch press having a frame, a slide, a driveshaft includin eccentric means for reciprocating said slide, comprising a housing secured to said frame, at least two balancing weights inclosed in said housing,

14 the first of said balancing weights being constructed to neutralize one-half of the unbalanced primary inertia forces as well as the rotational inertia forces, the second of said balancing weights being constructed to neutralize the remaining one-half of the unbalanced primary inertia forces; a first bevel gear, means for securing said first balancing weight to said first v bevel gear in a radially displaced position with respect to said driveshaft for counteracting the rotational inertia forces plus one-half of the primary inertia forces, a second bevel gear, means for securing said second balancing weight to said second bevel gear in a radially displaced position with respect to said drive shaft for counteracting the remaining one-half of the primary inertia forces, both said bevel gears being located within said housing in face-to-face and spaced relation and disposed coaxially with said driveshaft; an idler pinion meshing with both said bevel gears, and means for fastening said first bevel gear to said drive'shaft to rotate said bevel gears with their respective balancing weights in opposite directions but in synchronism with said driveshaft.

4. A counterbalancing device according to claim 3, including an internal gear ring secured to each of said bevel gears, a gear freely rotatable on the respective hubs of each of said bevel gears, a pinion meshing with each of said cooperating internal gear rings and gears for rotating said gears at twice driveshaft speed, an auxiliary balancing weight secured to each of said gears for counterbalancing the secondary inertia forces, said balancing weights being coincident at bottom dead center when the driveshaft is at top dead center.

FREDERICK K. MAUSSNEST.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,226,832 Webber May 22, 1917 2,127,317 Welch Aug. 16, 1938 2,182,988 Iseler Dec. 12, 1939 2,183,467 Sarazin Dec, 12, 1939 2,188,482 Parks Jan. 30, 1940 2,244,428 O'Leary June 3, 1941 2,248,182 Mateer July 8, 1941 2,284,515 Criswell May 26, 1942 2,293,915 Patterson Aug. 25, 1942 2,366,033 Johnstone Dec. 26, 1944 2,428,924 Albertson Oct. 14, 1947 

